Actuating mechanism for electromagnetic control devices



954 F. J. BYDALEK 2,637,274

ACTUATING MECHANISM FOR ELECTROMAGNETIC CONTROL DEVICES Filed Nov. 7, 1950 3 Sheets-Sheet 1 IN V EN TOR.

E d Jig mafia BY Jaw, [may lfl F. J. BYDALEK Aug. 24, 1954 ACTUATING MECHANISM FOR ELECTROMAGNETIC CONTROL DEVICES I .3 Sheets-Sheet 2 Filed Nov. 7, 1950 mmvrox I Egg d ag dazek I BY lamina ,dazzbrM Aug. 24; 1954 BYDALEK 2,687,274

ACTUATING MECHANISHFOR ELECTROMAGNETIC. CONTROL DEVICES Filed Nov. 7, 1950 3 Sheets-Sheet 3 /04 fig. 3

INVENTOR. Ji'gyd rfgydazek Patented Aug. 24, 1954 ACTUATING MECHANISM FOR ELECTRO- MAGNETIC CONTROL DEVICES Floyd J. Bydalek, Milwaukee, Wis., assignor to Milwaukee Gas Specialty Company, Milwaukee, Wis., a corporation of Wisconsin Application November '7, 1950, Serial No. 194,511

This invention relates, in general, to control devices, and has particular relation to an improved actuating mechanism for electromagnetic control devices.

While the particular device which I shall describe hereinafter in connection with the drawings is adapted for use for controlling a valve or the like for in turn controlling a heater or a cooling device or the like, it is to be understood that the device may be used for making, breaking, or changing the connections in one or more electric circuits, or for controlling other devices as suitable or desired.

The present invention may be more particularly characterized as relating to devices of the character disclosed and claimed in the copending application of Giiiord I. Holmes and Russell E. Matthews, Serial No. 180,482, filed August 19,-

8 Claims. (Cl. 251-76) example, to fully open position or other position i to which it is operated electromagnetically.

Another object of the invention is to provide a device in which relatively great movement is imparted to the actuated device after initiating movement or" such device, and more particularly a device in which the mechanical advantage is reduced, and increased movement is obtained after starting the movement of the actuated device with a hammer blow effect.

Another object of the invention is to provide actuating mechanism which will provide a relatively large mechanical advantage and increased force in the final movement of the actuated device to the position from which it is actuated electromagnetically; more particularly in the final movement of the valve to closed position whereby to produce a more powerful and efiective sealing of the valve against its seat.

Another object of the invention is to provide a device in which relatively great movement is imparted to the actuated device after initiating movement of such device in one direction with a hammer blow effect, and in which relatively great initial movement is imparted to theactuated device in the opposite direction followed by a relatively large mechanicaladvantage and increased force in completing such movement in the opposite direction.

Another object of the invention is to provide linkage and connector arm mechanism of simple, compact, and relatively inexpensive construction for accomplishing the advantageous results set forth, and linkage and connector arm mechansim which is combinable with the electromagneticaliy actuated control device of the'Carl Wolff application identified above.

Another object of the invention is to provide improved linkage and connector arm mechanism for use with an electromagnetically responsive control device utilizing the force of electromagnetic repulsion as distinguished from the force of electromagnetic attraction, and wherein the advantages of such a device will be obtained along with the other advantageous results provided by the present invention.

Another object of the invention is to provide improved linkage and connector arm mechanism for use with an electromagnetically responsive control device adapted for controlling a valve, switch, or other controlling device, for example, by a thermostat or other condition responsive device.

Another object of the invention is to provide improved linkage and connector arm mechanism for use with a repulsion type electromagnetically responsive control device comprising a winding provided with a core having a first core portion through which flux established by energization of the winding is adapted to pass, the core having, a second core portion provided with an air 7 gap, and there being flux diverting means operable to divert flux from the first core portion to the second core portion and the air gap, and a non-magnetic and conducting member positioned to travel freely in the air gap and in which the electric current is induced with accompanying repulsion of said member by the flux diverted to the second core portion and through the air gap by the flux diverting means.

Further objects and advantages of the invention will appear from the following detailed de: scription, taken'in connection with the accompanying drawings.

In the drawings:

Figure 1 1s a plan View of one form of device embodying the present invention, with the cover removed;

Figure 2 is a sectional view partially in elevation, taken through the electromagnetic operator substantially on the line 22 of Figure l, and showing the valve body in section; and

Figure 3 is a sectional view taken on the line 3-3 of Figure l.

Referring to the drawings, the embodiment of the invention therein illustrated comprises a valve body i having a fluid inlet 2 and a fluid out-' let 3. A valve member 54 cooperates with a valve seat 5 at the outlet 3 to control the flow of fluid through the valve body; for example, the flow of gaseous fuel to a burner (not shown), or any other fiuid. It will be noted that the controlled fluid tends to hold the valve member 54 closed. This may, of course, vary within the scope of the present invention.

The valve body I has an opening ii covered by a plate 1 which is secured in place over the opening 6, for example, by screws 3 (Figure 2). Sealing means 9 is preferably interposed between plate i and valve body I. The plate I is preferably formed of high specific resistance nonmagnetic material, such as stainless steel.

The particular magnetic core selected for illustration is of generally rectangular configuration, comprising a pair of parallel legs I! and I2 magnetically connected at spaced locations by parallel legs I3 and I4 disposed at right angles to the legs H and I2. An alternating current primary winding i5 is wound around the leg l4, and a secondary winding I6 is wound around the leg l3. It is to be understood, however, that either winding E5 or winding l6 may be the primary winding, and either winding may be the secondary winding without affecting the operation of the device. Electric power for energizing the winding i5 is supplied from a suitable source, for example, from line wires l1 and 18 of a suitable source of alternating current such as a household current supply line of the type which averages about 115 volts. The terminals of the winding R5 are connected to the line wires [1 and IS by conductors l8 and 20.

A cylinder is made up of square stock, and has a magnetic end 2!, a non-magnetic section 22,

and a magnetic section 23 separated from the magnetic section 2i by the non-magnetic section 22. The non-magnetic section 22 may be formed of non-magnetic high specific resistance material, such as stainless steel, or any suitable plastic, or other non-magnetic material. The legs H and 12 have projecting ends which abut at spaced locations against the magnetic end 2| and magnetic section 23, and are secured thereto, for example, by screws 2A and 25. The screws 24 cooperate with flanges 26 on the magnetic end 2i and with angular brackets 2'1 secured to the core ii! at 28. The screws cooperate with flanges 29 on magnetic section23 and with angular brackets 39 secured to core ID at 3!. The magnetic end 2| has an integral magnetic sleeve 32 which extends through the tubular non-magnetic section 22 and into the tubular magnetic section 23 with an annular space or air gap 33 therebetween.

A non-magnetic and electric conducting cup or sleeve 34 is free to travel in the annular air gap 33. The sleeve 34 is preferably made of electrolytic copper of high conductivity, and is necked or gathered in at one end to form a neck 35 of reduced diameter. An actuating member 36 is secured on neck 35 by a nut 31. A guide stem 38 is press-fitted as at 39 in the neck 35. The guide stem 38 rides in a bearing 40 pressfitted to the sleeve 32 at its right hand end as the device is shown in Figure 2. A bearing 4| is secured by a nut 42 to the left hand end of the guide stem 38. The bearing 4! may be formed of gear pinion stock, and has a smooth radius 43 to permit of low friction motion for the stem 38.

With the parts positioned as shown in Figure 2, the nut 33 is spaced from a projecting stem 44 to provide lost motion therebetween for a purpose which wil presently appear. The stem 44 is screwed and secured by a nut 45 to a crank 46. The actuating member 36 has an arm 41 which carries a pin 48. The pin 48 operates in a slot 49 in the crank 46 as will be hereinafter more fully described. The crank 46 is splined or keyed on an actuator shaft 59 which projects laterally from the position of the electromagnetic operator as shown in Figure 3, and has a valve operating arm 52 staked or otherwise secured to the shaft 53 at 53 so that turning of the shaft 50 will swing the arm 52 to open and close the valve 54. The position of the nut 31 relative to the stem M may be adjusted by replacing the lock shim 55 with lock shims of difierent thickness, or by using a plurality of shims.

The actuating member 36 may have an integral hook 58 for cooperation with the stem 44 in closing the valve 54 as will hereinafter appear. Screws 58 and 59, provided with suitable washers t6 and BI respectively, attach non-magnetic section 22 and magnetic section 23 to the plate 1'. Upon the absence of substantial magnetic flux in the gap 33, a spring 62 coiled about the stem 38 and acting against the bearings 40 and M urges the stem 38, and accordingly the sleeve 34, toward the left as the device is shown in Figure 2. Additional support for the magnetic core ID on the plate I may be provided by threaded posts 63, one of which is shown in Figure 3.

One end of the secondary winding l6 may be.

connected by a conductor 64, for example, with a fixed contact 65 of a thermostat 66. A conductor 61 connects the other terminal 68 of the thermostat 56 to the other end of the secondary winding it. a room or other space, or it may be placed where it will be subject to the temperature of a heater, or otherwise disposed as desired. It is also contemplated that the device 66, instead of being a temperature responsive thermostat, may be any other condition responsive means or other device for opening and closing the circuit of the secondary coil it, as suitable or desired.

. For the purpose of eliminating noise in the actuating mechanism between the actuator of the electromagnetically responsive device and the actuated device, a spring 10 is provided. This spring Hi may be in the form of a leaf spring of beryllium copper or other suitablematerial. It is fastened at one end between the nut 45 and crank 35, and has a V-shaped portion the free leg H of which is positioned for engagement with the pin 48 in the valve closing operation. When the actuator moves to the right from the position shown in Figure 2 the pin 48 contacts the spring leg H and the spring absorbs the vibrations so that no low level, high frequency noise can be heard.

In the operation of the device as shown in the drawings, the primary winding i5 is always energized from the line wires I! and IE or other suitable source of power. With the thermostat 66 in position separating its contact 68 from contact 65, the circuit for the secondary winding I6 is open and this winding is not energized. At this time the magnetic flux established by energization of the primary winding or coil 15 passes through the legs H, l2, I3, and 14 of the core l0, and very little flux passes through the air gap 33, for example, from the magnetic sleeve 32 of the member 2! to the magnetic sleeve section 23.

When, however, for example, the temperature to which thermostat 66 is responsive falls, the

The thermostat 66 may be positioned in 5, thermostat closes the contact 68 into engagement with contact 65. This closes the circuit of the secondary winding I6, and current is induced in this winding by the energization of the primary winding I5. This current induces a magnetic flux which opposes the magnetic flux established in leg I 3 by the primary winding I5. As a result the flux established by the winding I is diverted, for example, through the magnetic member 2|, sleeve portion 32 thereof, through air gap 33 to magnetic sleeve member 23, and through the member back through the leg I4 of the core I0.

Since the sleeve 34 is, in effect, a closed loop of good conductivity, there is induced in sleeve 34 an alternating current of opposite polarity to that impressed upon the winding I5. This alternating current so induced in turn induces an alternating flux field about the sleeve 34. The polarity of at least a portion of the field thus induced opposes the magnetic flux established by the energization of the winding I5. As a result the sleeve 34 is repulsed or repelled outwardly or to the right (Figure 2) out of the air gap 33. This causes movement of the actuator nut 3! and actuating member 36 to the right from the position shown in Figure 2.

As the sleeve 34 moves to the right, the nut 31 and stem 33 move to the right with the sleeve 34 and the nut 3'! strikes the head at the outer end of the stem 44 and swings the crank 46 clockwise (Figure 2) with accompanying clockwise rotation of the shaft 50. The lost motion between the nut 37 and stem 44 provides for engaging the stem 44 with a hammer blow effect, which overcomes any friction, sticking, or holding of the valve 54 closed, and initiates the opening movement of the valve 54. The pin 48, which moves to the right With the actuating member 36, travels freely in the slot 49 until the nut 31 strikes the head of the stem 44.

It will be noted that the mechanical advantage between the nut 3'! and the head of the stem 44 relative to the rotatable shaft 50 is considerably greater than the mechanical advantage between the pin 48 and the upper surface of the slot 49 as the device is shown in Figure 2. Hence in initiating opening of the valve 54 operated by the shaft 50, a high mechanical knock off force is obtained through the linkage mechanism. After the valve 5c is unseated, less force is required to move it to its fully opened position. Accordingly, the pin 48 strikes the upper inclined surface 13 of the slot 49 to impart with a given movement of the actuating member 36 increased swinging movement to the crank 46, and thereby increased and faster movement of the valve to its fully opened position is obtained.

position, the head of the produces a final closing force with a hammer effect and mechanical advantage similar to the knock off opening action between the nut 31 and stem 44 to complete the closing of the valve with a relatively great force.

While I have shown and described a flux diverting secondary winding I6 and associated core portion, it is to be understood that the secondary winding I6 and the cooperating core portion may be omitted within the scope of the present invention. In such case the thermostat or other means may be placed directly in the circuit between the primary winding and the line conductors I1 and I8. This will provide a line voltage device which is rendered operable by energization of the primary winding I5 and rendered inoperable by opening the circuit for the primary winding.

In the operation of the valve 54 to open posi tion, the pin 48 moves into contact with the free leg II of the V-shaped portion of the spring III. As a result, when the valve Ed is open, the spring it absorbs vibrations, and there will not be any low level, high frequency noise such as may otherwise occur by vibration of the pin 48 against the upper inclined surface at the outer end of the slot 49. The spring '50, instead of engaging the pin 43, may engage the outer surface of the slotted portion of the crank it to absorb the vibrations for the purpose set forth.

An annular or O-shaped ring I03 (Figure 3) of neoprene or other material which is resistant to gaseous hydrocarbons fits in an annular groove IBI in the shaft 5E3, and by cooperation with the shaft 50 and with the inner periphery of the opening in the member I forms a gas seal for pre- When the valve 54 reaches its fully opened position it will stay in such open position as long as magnetic flux, or at least sufficient magnetic flux, passes through the gap 33 to maintain the sleeve 34 in its repulsed or repelled position.

When thermostat 66 disengages contact 68 from contact 65, the magnetic flux established by energization of the winding I5 is again short-circuited through core legs II, I2, l3, and I4, and very little flux will exist in the air gap 33; Hence the spring 82 will then move the guide stem 38, and accordingly the sleeve 34, actuating member 36, and nut 31 toward the left as the device is shown in Figure 2. In such movement the pin 48 engages the lower surface of the slot 49 and causes rapid motion of the valve 54 in valve closing direction. After a predetermined motion toward closed position or just short of fully closed venting leakage of gas out along the shaft 50 from the interior of the valve body I. The 0 or ring seal Iilli has negligible rotational friction.

As shown more particularly in Figures 2 and 3, the electromagnetic control device is enclosed within a housing I I32 which may be removably secured in place to the plate or member I, for example, by screws !(23. The sides of the housing E92 may have longitudinal corrugations or folds I 134, and the outer surface of the housing I02 may have louvers or openings I85.

The embodiment of the invention shown in the drawings is for illustrative purposes only, and it is to be expressly understood that said drawings and the accompanying specification are not to be construed as a definition of the limits or scope of the invention, reference being had to the appended claims for that purpose.

I claim:

1. In a device of the class described, in combination, a pivoted actuating arm, an actuated device actuated by pivotal movement of said arm,

an electromagnetically operated actuator comprising a rectilinearly movable sleeve reduced at one end, an actuating member secured on the reduced end of said sleeve by a nut cooperable with the pivoted arm through a relatively long length thereof on movement of the sleeve in one direction, a hook carried by said actuating member and cooperable with the pivoted arm through a relatively long length thereof on movement of the sleeve in the opposite direction, there being lost motion between the nut and the pivoted arm in one direction and lost motion between the hook and said pivoted arm in the opposite direction, said actuating arm having an angular slot stem 44 is engaged by the hook 56 of the actuating member 36. This 7 member and having a pin operable in said slot and cooperating with said actuating arm to impart final movement to said arm in one direction and initial movement to said arm in the opposite direction each through a relatively short length of said arm.

2. In an operating mechanism of the class described, in combination, a pivoted arm, a control member operatively associated with said arm for movement from a first position to a second position by pivotal movement of said arm in one direction and from said second position to said first position by pivotal movement of said arm in the opposite direction, an actuator operable from a first position to a second position and from said second position to said first position, first actuator means on said actuator cooperating initially with said pivoted arm through a relatively long lever arm for initiating movement of said control member from said first position with relatively great mechanical advantage, and second actuator means on said actuator coaoting subsequently with said pivoted arm through a relatively short lever arm for imparting, after initial movement of said control member from said first position and with a given continued movement of said actuator toward said second position, increased and faster movement of said control member to said second position.

3. Operating mechanism according to claim 2 wherein said first actuator means is spaced from said pivoted arm when said actuator is in its said first position whereby, upon movement of said actuator toward said second position, to engage said pivoted arm with a hammer blow action to overcome any friction, sticking or holding of said control member in its said first position at commencement of movement of said control member from its said first position through said relatively great mechanical advantage.

4. Operating mechanism according to claim 2 wherein, in initial movement of said actuator from said second position to said first position, said second actuator means coacts with said pivoted arm through a relatively short lever arm for imparting with a given initial movement of said actuator toward said first position, increased and faster movement of said control member toward its said first position, and third actuator means on said actuator coaoting subsequently with said pivoted arm through a relatively long lever arm for completing movement of said control member to its said first position with relatively great mechanical advantage.

5. Operating mechanism according to claim 2 wherein, in initial movement of said actuator from said second position to said first position, said second actuator means coacts with said pivoted arm through a relatively short lever arm for imparting with a given initial movement of said actuator toward said first position, increased and faster movement of said control member toward its said first position, and third actuator means on said actuator coaoting subsequently with said pivoted arm through a relatively long lever arm for completing movement of said control member to its said first position with relatively great mechanical advantage, said third actuator means being spaced from said pivoted arm when said actuator is in its said second position whereby, upon movement of said actuator toward its said first position, to engage said pivoted arm with a hammer blow action for initiating completion of movement of said control member to its said first position through said relatively long lever arm with relatively great mechanical advantage.

6. In operating mechanism of the class described, in combination, a pivoted arm, a control member operatively associated with said arm for movement from a first position to a second position by pivotal movement of said arm in one direction and from said second position to said first position by pivotal movement of said arm in the opposite direction, an actuator operable from a first position to a second position and from said second position to said first position, first actuator means on said actuator coaoting initially with said pivoted arm through a relatively long lever arm for initiating movement of said control member from said first position with relatively great mechanical advantage, second actuator means on said actuator coaoting subsequently with said pivoted arm through a relatively short lever arm for imparting, after initial movement of said control member from said first position and with a given continued movement of said actuator toward said second position, increased and faster movement of said control member to said second position, said first actuator means being spaced from said pivoted arm when said actuator is in its said first position whereby, upon movement of said actuator toward its said second position, to engage said pivoted arm with a hammer blow action to overcome any friction, sticking or holding of said control member in its said first position at commencement of movement of said control member from its said first position through said relatively great mechanical advantage, said second actuator means coacting with said pivoted arm through a relatively short lever arm, for imparting with a given initial movement of said actuator toward said first position, increased and faster movement of said control member toward its said first position, and third actuator means on said actuator coaoting subsequently with said pivoted arm through a relatively long lever arm for completing movement of said control member to its said first position with relatively great mechanical advantage, said third actuator means being spaced from said pivoted arm when said actuator is in its said second position whereby, upon movement of said actuator toward its said first position, to engage said pivoted arm with a hammer blow action for initiating completion of movement of said control member to its said first position through said relatively long lever arm with relatively great mechanical advantage.

7. In operating mechanism of the class described, in combination, a pivoted crank having a slot therein, an arm operatively associated with said crank, a control member connected to said arm and movable to first and second positions, an actuator operable to first and second positions, first actuator means on said actuator initially engaging said crank through a relatively long lever arm for initiating movement of said control member toward its movement of said second position on said actuator toward its said second position, a pin constituting second actuator means on said actuator and operating in said crank slot and engaging onepart of said crank for imparting, after initial movement of said control member and with a given continued movement of said actuator to its second position, increased and faster movement of said control member to its second position, said pin engaging a different part of said crank and through a relatively short lever arm for imparting with a given initial movement of said actuator toward its said first position increased and faster movement of said control member toward its first position, and a hook constituting third actuator means on said actuator subsequently engaging said crank through a relatively long lever arm in movement of said actuator to its said first position for completing movement of said control member to its first position with relatively great mechanical advantage, there being lost motion between said first actuator means and said crank during initial movement of said actuator from its first position toward its second position, and there being lost motion between said hook and said crank during initial movement of said actuator from its second position toward its first position, whereby to initiate commencement of movement of said control member toward its second position and completion of movement of said control member toward its first position each with a hammer blow efiect.

8. In a device of the class described, in combination, a pivoted actuating arm, an actuated device actuated by pivotal movement of said arm, an actuator having a movable actuating member provided with first and second shoulder means, said first shoulder means being cooperable with said pivoted arm through a relatively long length thereof on movement of the movable member in one direction, and said second shoulder means being cooperable with said pivoted arm through a relatively long length thereof on movement of said actuating member in the opposite direction, there being lost motion between said first shoulder means and said pivoted arm in one direction and lost motion between the second shoulder means and said pivoted arm in the opposite direc tion, said actuating arm having first and second surface portions, and an abutment member connected to and movable with said actuating member, said abutment member being engageable with said surface portions and operating with said actuating arm to impart final movement to said arm in one direction and initial movement to said arm in the opposite direction each through a relatively short length of said arm.

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